EP0945653A1 - Joint à lèvres et compresseur - Google Patents

Joint à lèvres et compresseur Download PDF

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Publication number
EP0945653A1
EP0945653A1 EP99105758A EP99105758A EP0945653A1 EP 0945653 A1 EP0945653 A1 EP 0945653A1 EP 99105758 A EP99105758 A EP 99105758A EP 99105758 A EP99105758 A EP 99105758A EP 0945653 A1 EP0945653 A1 EP 0945653A1
Authority
EP
European Patent Office
Prior art keywords
solid lubricant
shaft
lubricant layer
seal
circumferential surface
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP99105758A
Other languages
German (de)
English (en)
Inventor
Masahiro Toyoda Jidoshokki Seisakusho Kawaguchi
Kenji Toyoda Jidoshokki Seisakusho Takenaka
Hirohiko Toyoda Jidoshokki Seisakusho Tanaka
Kazuya Toyoda Jidoshokki Seisakusho Kimura
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Toyota Industries Corp
Original Assignee
Toyoda Jidoshokki Seisakusho KK
Toyoda Automatic Loom Works Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Toyoda Jidoshokki Seisakusho KK, Toyoda Automatic Loom Works Ltd filed Critical Toyoda Jidoshokki Seisakusho KK
Publication of EP0945653A1 publication Critical patent/EP0945653A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/16—Sealings between relatively-moving surfaces
    • F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
    • F16J15/324—Arrangements for lubrication or cooling of the sealing itself

Definitions

  • the present invention relates to a compressor having a shaft seal for preventing leakage of fluid along a circumferential surface of a rotation shaft.
  • Japanese Unexamined Patent Publication No. 7-139633 describes shaft seal for preventing leakage of fluid along a circumferential surface of a rotation shaft.
  • the shaft seal is, for example, used for compressors.
  • the shaft seal includes a rubber seal element, which is ring-shaped to fit on the shaft of a compressor.
  • Refrigeration compressors include parts that slide against one another.
  • the sliding parts are lubricated by a lubricant that circulates in the compressor with a refrigerant.
  • a compressor is first started, especially a refrigeration compressor, an insufficient amount of lubricant is supplied between the seal element and the shaft surface.
  • the sliding contact between the shaft and the seal element abnormally wears the seal element. The wear lowers the sealing function of the shaft seal and shortens the life of the shaft seal.
  • the objective of the present invention is to provide a compressor with a shaft seal having high performance and long life of sealing function.
  • the present invention provides a shaft seal for sealing about the circumferential surface of a drive shaft.
  • a ring-shaped seal member is fitted on the drive shaft so that leakage of fluid along the circumferential surface of the drive shaft is prevented.
  • the seal member has an annular lip that is urged toward the circumferential surface.
  • a solid lubricant layer is provided between the annular lip and the circumferential surface.
  • variable displacement compressor according to a first embodiment of the present invention will now be described in reference to Figs. 1-3.
  • a front housing 12 and a rear housing 19 are joined to a cylinder block 11.
  • a control chamber 121 is formed in the front housing 12.
  • a vehicle engine (E) rotates a drive shaft 13, which is supported between the cylinder block 11 and the front housing 12.
  • a swash plate 14 is supported to rotate integrally with the drive shaft 13 and to incline with respect to the drive shaft 13.
  • the swash plate 14 moves between a maximum inclination position, which is shown by a full line in Fig. 1, and a minimum inclination position, which is shown by broken line in Fig. 1.
  • the cylinder block 11 includes cylinder bores 111. Each cylinder bore 111 accommodates a piston 17. Each piston 17 defines a compression chamber 112 in the associated cylinder bore 111. Each piston 17 is coupled to a swash plate 14 through a pair of shoes 18. To compress refrigerant gas, the rotation of the swash plate 14 is converted to reciprocation of each piston 17 through the shoes 18.
  • the rear housing 19 includes an intake chamber 191 and a discharge chamber 192. When the piston 17 moves from the top dead center to the bottom dead center, refrigerant is drawn from the intake chamber 191 to the compression chamber 112 through an intake port 21, which opens a flexible intake valve 20. When the piston 17 moves from the bottom dead center to the top dead center, refrigerant compressed in the compression chamber is discharged into the discharge chamber 192 through a discharge port 23, which opens a flexible discharge valve 22.
  • the intake passage 16 is connected to the discharge chamber 192 through an external refrigerant circuit 24.
  • the external refrigerant circuit 24 includes a condenser 25, an expansion valve 26, and an evaporator 27.
  • the expansion valve 26 controls the flow amount of refrigerant through the circuit 24 in accordance with changes of temperature in the evaporator 27.
  • An accommodation chamber 113 is formed in the center of the cylinder block 11.
  • the intake chamber 191 is connected to the intake passage 16 through the accommodation chamber 113.
  • a cylindrical shutter 15 is slidably fitted in the accommodation chamber 113.
  • the shutter 15 supports the rear end of the drive shaft 13 through a bearing 46.
  • the shutter 15 moves axially with the inclination of the swash plate 14. That is, when the swash plate 14 is at the minimum inclination position shown by the broken line in Fig. 1, the shutter 15 moves axially to close the intake passage 16. That is, the right end of the shutter 15 (as viewed in Fig. 1) abuts against the exit of the passage 16 to seal it.
  • the shutter 15 is axially spaced from the exit thus opening the intake passage 16.
  • the compressor further includes an electromagnetic valve 29.
  • a supply passage 28, which connects the discharge chamber 192 to the control chamber 121, supplies refrigerant from the discharge chamber 192 to the control chamber 121.
  • the electromagnetic valve 29 is located in the middle of the supply passage 28.
  • a controller 30 controls magnetizing and demagnetizing the electromagnetic valve 29 in accordance with the temperature of a passenger compartment, which is detected by a temperature detector 31, and a target temperature set by a temperature adjuster 32.
  • the refrigerant in the control chamber 121 flows to the intake chamber 191 through a passage 131 in the drive shaft 13, the inside of the shutter 15, a restricting passage 151 in the shutter 15, and the accommodation chamber 113.
  • a valve body 291 closes the supply passage 28.
  • the refrigerant in the discharge chamber 192 does not flow to the control chamber 121 and the refrigerant in the control chamber 121 flows to the intake chamber 191 through the passage 131. Accordingly, the control pressure in the control chamber 121 is reduced and the difference between the control pressure and the intake pressure in the intake chamber 191 becomes small, thus increasing the inclination of the swash plate 14.
  • the valve body 291 opens the supply passage 28.
  • the refrigerant in the discharge chamber 192 flows to the control chamber 121.
  • the control pressure in the control chamber increases and the difference between the control pressure and the intake pressure increases, thus reducing the inclination of the swash plate 14.
  • the shutter 15 closes the intake passage 16. Then, the flow of refrigerant from the intake passage 16 to the intake chamber 191 through the accommodation chamber 113 is stopped. Accordingly, little or no refrigerant is discharged from the compressor to the external refrigerant circuit 24.
  • a seal chamber 122 for a ring-shaped seal is formed in the front housing 12 at a position corresponding to the circumferential surface of the front end of the drive shaft 13.
  • a shaft seal 33 is accommodated in the seal chamber 122.
  • the shaft seal 33 includes a ring case 34, a rubber seal ring 35, which is fitted in an outer annular recess 341 formed about the ring case 34, a pair of ring-shaped metal retainers 36, 37 located inside the ring case 34, a first rubber lip ring 38 retained in the retainer 36, a second fluororesin lip ring 39 retained in the retainer 37, and a ring-shaped metal retainer 40.
  • the second lip ring 39 is, for example, made of polytetrafluoroethylene.
  • the ring case 34 contacts an inner wall 123 and is retained in the accommodation chamber 122 by a snap ring 41.
  • the seal ring 35 is held in contact with the outer annular recess 341 and a cylindrical surface 124 of the seal chamber 122.
  • the circumferential rims of the retainers 36, 37, the first lip ring 38, and the second lip ring 39 are retained in an iner annular recess 342 inside the ring case 34.
  • the retainer 40 is located between the first lip ring 38 and the second lip ring 39.
  • Fig. 2 shows the shaft seal 33 prior to installation on the drive shaft 13.
  • Fig. 1(a) when the shaft seal 33 is fitted on the drive shaft 13, the inner circumferential portions of the first lip ring 38 and the second lip ring 39 contact the circumferential surface 132 of the drive shaft 13.
  • a first solid lubricant layer 42 is attached to a sliding contact portion 381 of the first lip ring 38, which slides on the circumferential surface of the drive shaft 13.
  • a second solid lubricant layer 43 is attached to a sliding contact portion 391 of the second lip ring 39, which slides on the circumferential surface 132 of the drive shaft 13.
  • the sliding contact portion 391 of the second lip ring 39 includes a spiral groove 392.
  • the second lip ring 39 is a flat ring prior to installation on the shaft seal 33.
  • the spiral groove 392 is formed as shown in Fig. 3(b). The spiral groove 392 functions to return lubricant oil, which would otherwise leak from the control chamber 121 along the circumferential surface 132 of the drive shaft 13 to the exterior of the compressor.
  • the solid lubricant layers 42, 43 are made of a mixture that includes molybdenum disulfide, graphite, and polyamideimide thermosetting resin. Molybdenum disulfide and graphite are excellent solid lubricants and polyamideimide thermosetting resin function as adhesive.
  • the mixture is applied on the sliding contact portion 381 of the first lip ring 38 and the sliding contact portion 391 of the second lip ring 39 and is dried, thus forming the solid lubricant layers 42, 43.
  • the mixture is applied using spraying or pad printing.
  • the solid lubricant material may be one of or a combination of a polymer (such as ethylenetetrafluoride), molybdenum desulfide, graphite, tungsten disulfide, lead oxide, boron nitride, and a soft metal (such as lead, gold, indium, tin).
  • a polymer such as ethylenetetrafluoride
  • molybdenum desulfide such as ethylenetetrafluoride
  • graphite molybdenum desulfide
  • tungsten disulfide graphite
  • lead oxide tungsten disulfide
  • lead oxide such as aluminum oxide
  • a soft metal such as lead, gold, indium, tin
  • Polyamideimide thermosetting resin may be used as adhesive.
  • the soft metals such as lead, gold, indium, and tin may be plated.
  • the present invention has the following advantages.
  • the present invention will further be embodied as follows.
  • the second lip ring 39 is made of fluororesin and is less likely to wear than the first lip ring 38, which is made of rubber.
  • the rubber first lip ring 38 primarily seals the control chamber 121. Therefore, the sealing function of the shaft seal 33 is affected more by wear of the first lip ring 38 than by wear of the second lip ring 39.
  • the first solid lubricant layer 42 may be provided only on the first lip ring 38. In this case, wear is postponed for relatively long time.
  • the solid lubricant layer 42 may be provided only on the second lip ring 39. In this case, the wear of the second lip ring 39 and heat generation of the sliding contact portion 391 of the second lip ring 39 are reduced. As a result, deterioration of the adjacent first lip ring 38 is reduced and the life of the shaft seal 33 is extended.
  • the solid lubricant layer 42 is applied to the whole surface of the first lip ring 38. Further, the solid lubricant layer 43 is applied to the whole surface of the second lip ring 39.
  • the solid lubricant layer 44 is applied to the whole surface of the shaft seal 33 after its assembly.
  • a rotating solid lubricant layer 45 is provided on the circumferential surface 132 of the drive shaft 13 along a section contacting the first and the second lip rings 38, 39.
  • the rotating solid lubricant layer 45 is preferably tin plating.
  • the rotating solid lubricant layer 45 prevents the first and the second lip rings 38, 39 from abnormally wearing. Also, the solid lubricant layer 45 reduces the heat generated by the second lip ring 39 and thus delays the deterioration of the adjacent first lip ring 38.
  • the rotating solid lubricant layer 45 may be provided only on the section of the circumferential surface 132 contacting the first lip ring 38 or only on that contacting the second lip ring 39.
  • the rotating solid lubricant layer 45 on the drive shaft 13 may be made of the same material as the solid lubricant layers 42, 43 on the lip rings 38, 39, that is, a mixture of molybdenum disulfide, graphite lubricant, and polyamideimide thermosetting resin.
  • the rotating solid lubricant layer 45 may be provided on the whole circumferential surface 132 of the drive shaft 13. That is, the rotating solid lubricant layer 45 may be provided on the circumferential surface 132 contacting the swash plate 14 and contacting the bearing 46 in the shutter 15.
  • the rotating solid lubricant layer 45 may further be provided on the drive shaft 13.
  • the solid lubricant layers 42, 43, 44 which are made of a mixture of molybdenum disulfide, graphite, polyamideimide thermosetting resin, make sliding contact with the rotating solid lubricant layer 45, which is tin plating.
  • the sliding contact between solid lubricant layers having different compositions prevents fusion adherence during sliding, and the reliability and durability of the shaft seal 33 are improved.
  • the shaft seals of the present invention may be located between the shaft and any part inside a compressor and the seals may be used with any type of compressor.
  • the application of the present invention is not limited to compressors.
  • the present invention is applied to any apparatus where there is a need to prevent leakage of fluid along a drive shaft.
  • a shaft seal (33) is installed on the circumferential surface (!32)of a drive shaft (13).
  • a first lip ring (38) made of rubber and a second lip ring (39) made of fluororesin are urged toward the drive shaft (33) to prevent leakage of fluid along the circumferential surface of the drive shaft (13).
  • Each lip has a contact portion (381, 391) facing the circumferential surface of the drive shaft (33).
  • a solid lubricant layer (42, 43) is provided on the contact portions (381, 391) to reduce friction and to extend the life of the seal (33).
  • the solid lubricant may also be formed on the surface of the drive shaft (13).

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Compressor (AREA)
  • Sealing With Elastic Sealing Lips (AREA)
  • Sealing Of Bearings (AREA)
EP99105758A 1998-03-23 1999-03-22 Joint à lèvres et compresseur Withdrawn EP0945653A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP7419098 1998-03-23
JP10074190A JPH11270696A (ja) 1998-03-23 1998-03-23 軸封装置及び圧縮機

Publications (1)

Publication Number Publication Date
EP0945653A1 true EP0945653A1 (fr) 1999-09-29

Family

ID=13540015

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99105758A Withdrawn EP0945653A1 (fr) 1998-03-23 1999-03-22 Joint à lèvres et compresseur

Country Status (2)

Country Link
EP (1) EP0945653A1 (fr)
JP (1) JPH11270696A (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1008775A2 (fr) * 1998-12-11 2000-06-14 SKF INDUSTRIE S.p.A. Dispositif d'étanchéite pour paliers
EP1004801A3 (fr) * 1998-11-24 2001-02-28 Mitsubishi Cable Industries, Ltd. Joint d'étanchéité pour arbre rotatif
US6592337B2 (en) 2000-11-29 2003-07-15 Kabushiki Kaisha Toyota Jidoshokki Shaft seal of a lip type with fluid guiding components having the same
EP1431632A2 (fr) * 2002-12-16 2004-06-23 Carrier Corporation Bague d'usure pour joint à lèvre
EP1304515A3 (fr) * 2001-10-19 2004-08-11 Eagle Industry Co., Ltd. Dispositif d'étanchéité
EP2175136A1 (fr) * 2007-07-18 2010-04-14 Sanden Corporation Joint d'étanchéité d'arbre

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003097722A (ja) 2001-09-27 2003-04-03 Denso Corp 軸封装置
JP2008232014A (ja) * 2007-03-20 2008-10-02 Sanden Corp 圧縮機

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4109921A (en) * 1976-05-27 1978-08-29 Taunus-Armaturen Gmbh Seal for pistons and piston rods of cylinder-type actuators
DE3618786A1 (de) * 1986-06-04 1987-12-10 Goetze Ag Flachdichtung, insbesondere fuer verbrennungskraftmaschinen
US4808323A (en) * 1986-10-01 1989-02-28 Federal-Mogul Corporation Non-deleterious dry film lubricant coating composition, rubber sealing element coated therewith; and method of
US5171622A (en) * 1989-12-01 1992-12-15 Glyco-Metall-Werke Daelen & Hofmann Kg Composite laminate for sliding elements having a running or sliding layer to which a conforming filler-containing layer is applied
JPH07139633A (ja) 1993-11-16 1995-05-30 Mitsubishi Cable Ind Ltd 回転軸シール
WO1998002681A1 (fr) * 1996-07-17 1998-01-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Structure d'etancheite pour arbre de compresseur

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4109921A (en) * 1976-05-27 1978-08-29 Taunus-Armaturen Gmbh Seal for pistons and piston rods of cylinder-type actuators
DE3618786A1 (de) * 1986-06-04 1987-12-10 Goetze Ag Flachdichtung, insbesondere fuer verbrennungskraftmaschinen
US4808323A (en) * 1986-10-01 1989-02-28 Federal-Mogul Corporation Non-deleterious dry film lubricant coating composition, rubber sealing element coated therewith; and method of
US5171622A (en) * 1989-12-01 1992-12-15 Glyco-Metall-Werke Daelen & Hofmann Kg Composite laminate for sliding elements having a running or sliding layer to which a conforming filler-containing layer is applied
JPH07139633A (ja) 1993-11-16 1995-05-30 Mitsubishi Cable Ind Ltd 回転軸シール
WO1998002681A1 (fr) * 1996-07-17 1998-01-22 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Structure d'etancheite pour arbre de compresseur

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1004801A3 (fr) * 1998-11-24 2001-02-28 Mitsubishi Cable Industries, Ltd. Joint d'étanchéité pour arbre rotatif
EP1008775A2 (fr) * 1998-12-11 2000-06-14 SKF INDUSTRIE S.p.A. Dispositif d'étanchéite pour paliers
EP1008775A3 (fr) * 1998-12-11 2001-07-11 SKF INDUSTRIE S.p.A. Dispositif d'étanchéite pour paliers
US6592337B2 (en) 2000-11-29 2003-07-15 Kabushiki Kaisha Toyota Jidoshokki Shaft seal of a lip type with fluid guiding components having the same
EP1211444A3 (fr) * 2000-11-29 2004-01-07 Kabushiki Kaisha Toyota Jidoshokki Joint d'étanchéité d'arbre de type à lèvre et éléments de guidage ayant un tel joint
EP1304515A3 (fr) * 2001-10-19 2004-08-11 Eagle Industry Co., Ltd. Dispositif d'étanchéité
EP1431632A2 (fr) * 2002-12-16 2004-06-23 Carrier Corporation Bague d'usure pour joint à lèvre
EP1431632A3 (fr) * 2002-12-16 2004-07-21 Carrier Corporation Bague d'usure pour joint à lèvre
EP2175136A1 (fr) * 2007-07-18 2010-04-14 Sanden Corporation Joint d'étanchéité d'arbre
EP2175136A4 (fr) * 2007-07-18 2010-10-06 Sanden Corp Joint d'étanchéité d'arbre

Also Published As

Publication number Publication date
JPH11270696A (ja) 1999-10-05

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